Filling machine



FILLING MACHINE Original Filed June 18, 1934 9 Shets-Sheet 1 a H ll!!! H. R. PHILLIPSET AL Aug. 4, 1936.

FILLING MACHINE Original Filed June 18, 1934 9 Sheets-Sheet 2 Aug. 4, 1936. H. R. PHILLIPS ET AL. 2,049,722

FILLING MACHINE Original Filed June 18, 1934 9 Sheets-Sheet 3 Aug. 4, 1936.

FILLING MACHINE 9 Sheets-Sheet 5 Original Filed June 18, 1934 aywilwntors M y, (Ittomeu 1 2 a E \f w N I 2 5a P w 0 in n l wnlwii 7 2 W Y (I (I .i

H. R. PHILLIPS ET AL. 21,49,722

FILLING MACHINE Original Filed June 18, 1934 9 Sheets-Sheet 6 Ill/Ill Aug. 4, 1936. H. R PHILLIPS ET AL 2,049,722

FILLING MACHINE 9 Sheets-Sheet 7 Original Filed June 18, 1934 .1 Jill/ll ZWIWU Aug. 4, 1936. H. R PHILLIPS ET AL' 2,049,722

FILLING MACHINE Original Filed June 18, 1934 9 Sheets-Sheet 8 3nvcntors My 2w Aug. 4, 1936. H. R. PHILLIPS ET AL 2,049,722

FILLING MACHINE Original Filed June 18, 19.34 9 Sheets-Sheet 9 & I Q V I m i a j 1/ i If 27,1

QnveqtorS Patented Aug. 4, 1936 PATENT OFFICE FILLING MACHINE Harley R. Phillips, Oak Park, and Henry J. Clarke. Chicago, Ill., assignors to Mojonnier Bros. 00., a corporation of Illinois Original application-June 18, 1934, Serial No.

Divided and this application June 21,

1935, Serial No. 27.636

4 Claims. (01. 226-97) The present invention relates to filling machines, and particularly filling machines for taking measured charges of a commodity from a bulk supply and depositing the same in cartons, cups or like containers which are commonly fed to the machine, filled with a commodity, capped and discharged automatically.

The invention is directed especially to the filling of cartons and the like at a greatly increased speed over prior ways of performing the same functions, in contrast to the measuring and filling operations. All the features having to do with the latter operations are claimed 'in our prior parent application Serial Number 731,078, filed June 18, 1934, out of which the application is carved as a division. The features having to do with the filling and handling of the cartons, together with the effective adjustments employed are covered by the claims of the present case.

The invention has to do with the handling of the container at the time it is being filled with the commodity. As is common with machines of this class the containers travel in a circuitous path from the point at which they are placed in the machine to a filling position and then on to a delivery point.

According to this feature of the invention the container is thrust upward against the lower end of the spout of the filling mechanism and held there at the time it is being filled with the commodity. The novel arrangement of parts by which this result is obtained is such that when the container has been brought into a position directly below the nozzle of the filling mechanism a movable member beneath the container forces it upward into engagement with the nozzle and yet does not dislocate it with reference to the 4 conveying means but maintains it so that when the container is properly filled it may drop back into its normal position in the conveyer and be carried forward to the delivery point.

The invention furthermore has to do with the production of an ejector mechanism for delivering the filled and capped or covered container from the conveyer when the delivery point is reached.

In carrying out this feature of the invention the ejector which comprises a vertically movable member is thrust upward against the bottom of the filled and closed container and engages the same with sufficient force to free it from its seat in the conveyer and tumble it therefrom into a chute or other receptacle from which it may be taken and handled as desired. This ejector works in timed relation with movements of the conveyer and comes into play periodically to eject the filled containers successively as they present themselves at the delivery point.

Another feature of the invention resides in the indexing mechanism by which the conveyer which is commonly a rotating table is accurately set with reference to the various devices with which it is associated. Thus, where there is a container feeder and a container capper associated with filling mechanism, it is important that the table be accurately set so that a container in a given position on the table will present itself in proper position beneath the filling mechanism and again beneath the capping mechanism.

To the end that this may be properly accomplished an actuating drum cam is employed to rotate the table step by step and means are provided for adjusting this drum cam lengthwise of its axis so as to bring about a proper setting of the conveying table relative to its several operating positions, that is to say, relative to its container feeding position, its filling position, its capping position and its delivery position.

The invention also contemplates other features and advantages which will more fully appear upon consideration of the detailed disclosure.

The novel features of the invention have been worked out in the devising of a filling machine for the handling of plastic materials such as partially frozen ice cream, water ices and the like. The invention will therefore be described in that connection although it will be understood that the same is of broader application and need not be limited to the ice cream field.

The various features and advantages of the invention will be fully understood upon reference to the following detailed description taken in connection with the accompanying drawings, while the scope of the invention will be particularly pointed out in the appended claims.

In said drawings, Fig. l is a perspective view of a filling machine constructed and arranged in accordance with the present invention; Fig. 2 is a side elevation of the same machine viewed from the right as the parts are shown in Fig. 1,- Fig. 3 is a transverse vertical section through the machine, the plane of section being indicated by the line 3--3 of Fig. 2; Fig. 4 is a central vertical section taken at right angles to the view in Fig. 3, the plane of section being indicated by the line lt of Fig. 3'; Fig. 5 is a transverse vertical section through the machine, the plane of section being indicated by the line 5-5 of Fig. 4 Fig. 6 is a horizontal section taken on a plane indicated Cil view of the directing valve of the commodity measuring mechanism of the machine; Fig. 8 is a perspective view of a clutch pin forming part of the main clutch of the machine which operates to transmit power to drive the commodity feeding mechanism; Fig. 9 is a sectional view through the feeding mechanism, the plane of section being indicated by the line 9-9 of Fig. 4; Fig. 10 is a sectional view through one set of feeding cylinders showing the relation of the same to other parts of the machine, the plane of section being indicated by the line lO-lll of Fig. 9; Fig. 11 is an end elevation of one set of cylinders with certain portions of the adjacent structure shown in section, the plane of section being indicated by the line lI-ll of Fig. 9; Fig. 12 is a plan view of the directing valve casing, the position of the view being indicated by the line l2-l2 and the associated arrows of Fig. 9; Fig. 13 is a diagrammatic view illustrating the trip mechanism for operating the main clutch of the machine to'bring about the commodity feeding operations only when a container is properly positioned to receive the charge of the commodity resulting from such operation; Fig. 14 is a front elevation of the central portion of the machine, illustrating more particularly the mechanisms for operating the container holding table, the container feeder, the capper and the ejector; and Fig. 15 is an inverted plan view of the same portion of the machine, parts being shown in section taken on a plane indicated by the line |5-l5 of Fig. 14. Throughout these views like characters refer to like parts. In a few words, the machine consists of a base A, a main frame or casing B located upon the base, commodity measuring mechanism C located at the top of the main frame, a commodity hopper D for holding the commodity in bulk above the measuring mechanism, a rotary table mechanism E positioned at the front of the machine with its table located so as to receive charges from the measuring mechanism, and, associated with this table, a feeder F for supplying empty containers to the table, a capper G for capping the filled containers while still held by the table, and a delivery chute H into which the closed filled containers are deposited by ejector mechanism I.

The driving motor M is located within the base A and operates through suitable gearing to drive the measuring mechanism C and the table mechanism E. Thetrain of gearing for driving the mechanism C includes a clutch N which is the mainclutch of the machine. This clutch is controlled by trip mechanism 0 organized so as to be operated or not in accordance with the presence or absence of properly positioned containers 1? upon the table of the mechanism E. This train of gearing includes a crank disk Q which cooperates with suitable connecting rods and associated links to reciprocate the pistons and oscillate the directing valve of the measuring mechanism C. The other train of gearing which drives the table mechanism E is arranged to actuate a cam shaft R at the front of the machine and this shaft gives an intermittent step by step travel to the table which carries the containers. As this table advances it receives the containers P from the feeder F, these containers are filled one after the other with the commodity by the mechanism C, caps are applied to the filled containers by the capper G, and, finally, the filled andcapped containers are ejected from the table into the chute H by the ejector mechanism 1.

Going over these principal elements of the ma- I chine more in detail, we find that the base A is a shell of metal, preferably cast iron, having a general triangular form in plan with an adjustable foot 20 at each corner of the triangle. Each foot 20 is made adjustable so that the base may be set in a level position upon an irregular floor or other support. The adjustment is obtained in each case, by screwing the foot 20 into or out of the ad-.

jacent portion of the base and then holding itv in adjusted position by a lock-nut 2|. Obviously, the feet 20 may be made up in different ways, it being important only that it be possible to accurately level the base when setting up the machine. The upper portion of the base A is drawn in so as to fit against the under side of the frame B which is of box like formation and of considerably smaller overall horizontal dimensions than the base A. The frame B may be secured to the base A in different ways, as by means of bolts, a few of which, designated 22, are shown. To assist in connecting the two frame elements A and B, the base may be flanged at various points, as indicated by the flanges 23. These, however, are all matters of detail which may be worked out as desired by the designer and manufacturer.

The main frame B is, as stated, of box like formation and is preferably ametal casting. It comprises several brackets, extensions and other parts which may be better referred to when describing other parts of the machine which it supports.

The measuring mechanism C comprises a central metal casing or frame 24 which is secured on the forward side of a vertical wall 25 which extends upward from the main frame B and is laterally strengthened by webs 26 integral with the wall 25 and other adjacent portions of the frame B. The frame 24 constitutes the valve casing proper of the directing valve of the meas uring mechanism C. It may be secured to the wall 25 in any desired way, but, preferably, this is acomplished by machine bolts 21, 28 extending through the wall 25 into threaded engagement with portions of the casing 24, as clearly illustrated.

The central member 24 of the mechanism C is preferably composed of metal suited to the commodity being handled and in its opposite ends it is provided in the illustrated embodiment, with three bores symmetrically arranged, as clearly shown in Fig. 10, and into these circular openings are fitted two sets of cylinders, three at each end of the member 24. The cylinders, designated 32 at the left and 33 at the right, as the parts are viewed in Figs. 3 and 9, are firmly secured in place by welding or otherwise and provide smooth bores on the interior for the travel of the associated pistons 34 in the case of cylinders 32, and 35 in the case of cylinders 33. The pistons 34 are provided with piston rods 36 and the pistons 35 are provided with piston rods 31.

Since, in the present embodiment, it is intended that three different commodities, or three difiereni; flavors of the same commodity, as for instance three different flavors of ice cream, are to be fed by the machine, the valve casing 24 has three pockets or channels 38 bounded by the walls of the casing 24 and intervening partitions 39. These are located near the top of the member 24 above the cylindrical chamber in which the directing valve 40 fits. These partitions 39 and the cooperating walls 4| determine the path of travel of the diiferent'fiavors, or ingredients, as they pass into the chambers of the valve 40, and, as we shall see, they are kept separate until after they have passed the valve. They then pass through suitable openings, as the openings 42, located beneath the valve 60 in the bottom of the casing 24, as clearly shown in Fig. 11. These openings 42 may join in a large delivery opening 43. The difierent flavors, or ingredients, furnished by the separated passages will then be discharged into the container below in practically the same relation to each other as they occupy when they emerge from the passages 42. Of course, if desired the partitions 44 which lie between the passages 42, might be extended to a lower point to maintain still further the separation mentioned. In practice, however, it is found that the structure illustrated is quite satisfactory.

The valve 40 which occupies the cylindrical space in the casing member 24, is substantially cylindrical in general outline, as clearly shown in Fig. 7. This valve, however, is divided up into passages 48 on the one side and passages 49 on the other. These passages are provided by cutting away material from opposite sides so as to leave a central web 50 which extends axially of the valve and has thickened end portions 5! which strengthen the structure. In forming the chem-- nels 48 and 49 almost 180 degrees of the material is cut away on each side of the'web 50. The channels 48 are bounded by the end walls 52, 53 and the intermediate partitions 5 5. In

like manner the channels 49 are bounded by the same end walls 52, 53 and intermediate partitions 55. The member 24 is also provided with passages 51 which lead from the forward ends of the cylinders to the cylindrical seat of the valve til. The passages leading from the cylinders 33, are shown more particularly in Fig. 11, and from an inspection of that view, it will be seen that they are bounded by the end walls 58 and the intervening partitions 59. The same arrangement of passages 51 is provided in association with the cylinders 32, and the same are similarly bounded. The cylindrical surface in which the passages 38 and 51 terminate, form the cylindrical seat of the valve 40.

The valve 60 is held in place by an end plate 60 which slips over a stud 6i formed on one end of the valve. The plate Bil is of suflicient size to extend beyond the valve and engage with the adjacent walls of the valvecasing 26, as shown perhaps most clearly in Fig. 4. The plate 60 cooperates with a flange 62 formed at the opposite end of the valve. When it is desired to remove the valve 40, the plate 6!) is removed and the valve drawn through the cylindrical opening in the casing 26 as will be obvious. Normally a frictional engagement is provided between the valve to and its casing E l by the use of a coiled spring 63 which surrounds the stud BI and bears at one end against the plate 60 and at the other end against the head of a thumb screw 6% which has its shank threaded into a suitable opening in the end of the stud. By adjusting the screw St the tension upon the spring 63 may be varied to increase or decrease the friction between the valve and its casing and hence decrease or increase the ease of rotation of the valve. The end of the valve wherein the flange 62 is located is provided with a crank arm 65 and it is through this crank arm 65 and the associated link 66 that the valve to is oscillated to bring it into its different commodity directing positions.

These positions, as clearly shown in Figs. 3 and 9, are such as to place the cylinders in communication either with the supply hopper D or with the outlet 43. Thus, in Fig. 3, the hopper is in direct communication with the cylinders 33, and the cylinders 32 are in direct communication with the outlet 43; while in Fig. 9 the hopper is in direct communication with the cylinders 32, and the 5 cylinders 33 are in direct communication with the outlet 43. Because of the channels 48. 49 of the valve alining with the inlet passages 38 and the cylinder passages 51, it will be obvious that in each one of these positions there are three parallel 10 paths through the valve from the hopper into one set of cylinders and from the other set of cylinders to the outlet. In this way, as before explained, the diflerent flavors or ingredients of'the commodity are kept separate until the delivery point of the valve is reached.

The lower end of the valve casing is provided with a plate lil which is-secured in position by suitable screws 1 I vJust above this plate the inner surface of the member 24 is cut away so as to 20 provide grooves 12 in which a. reciprocating cutoff plate l3 travels to cut oil the stream of the commodity, such as icecream, in a clean fashion at the instant that the carton. beneath is filled and while the table is bringing another carton into 25 filling position. The plate has a, central opening it in it, which alines with the valve discharge opening 43 whenever the carton is in position to be filled- Just as the container is filled, the valve 40 moves to its new positionand in doing so moves the plate i3 and thereby cuts off any of the commodity which may be adhering to the spout and allows it to drop into the container. While the table mechanism E operates to bring a new container into filling position, the plate It closes, and 3 maintains closed, the opening t3, but, as soon as the valve 40 reaches its alternate position, the opening i4 again is in registry with the opening 43 ready for the discharge of commodity into the new container. The two positions of the valve t0, shown in Figs. 3 and 9, are established when the projection E5 on the valve to engages-either of the stops 16, shown in dotted lines in Fig. 9. The stops it are projections on a portion of the valve casing M. For the valve position of Fig. 9, the stop l5 engages stop 16 at the right, while for the position of Fig. 3, the stop '65 engages the stop it at the left.

The necessary reciprocations are given to the plate l3 through link mechanism which is actuated from the oscillating valve Mi. This mechanism includes a link H which is pivotally connected at one end to the crank 65 of the valve and at the other end to an intermediate point of a link 18. The latter is pivoted at M to a fixed portion of the machine and its free end is pivoted at to a two part adjustable link Bl. The parts of this link are an angular rod 82 and'a blocklike member 83. The rod 82 has one end threaded into the block-like member 83. The angular end to. 8d of the rod 82 passes through an opening in one end of the plate [3. By threading the rod 92 into and out of the block 8 3, the length of the two part link may be adjusted so as to enable the plate l3 to be properly set. A nut threaded 65 upon the rod 82 is adapted to abut against the end of the block 83 and thus fix the adjustment of the parts relative to each other. With this link connection it will be seen that as the valve M oscillates between its stops it, the crank 65-70 will pass from a, low point illustrated in Fig. 3. to a. high point illustrated in Fig. 9, and in so doing will move the plate 13 from an open position through a closed position and back again to an open position. This movement cuts oil any 75 or other suitable cooling material taken in through an intake pipe 94 and withdrawn through an outlet pipe 95, all as is common in the art where ice cream is the ingredient handled. In this embodiment angle irons 96 are used in the frame work of the hopper D. A cover 91' of suitable metal construction is also employed. \In certain 1 instances the cover 91 may be given an inclined housing 98 having an opening 99 at one end for g the passage of one end of a lever I used to agitate the. material in the hopper as is sometimes done in hoppers'of the kind, especially where ice cream is the commodity handled. The lever I00 is given a rocking motion by a connecting rod IOI which is reciprocated through the agency of a rocker arm I02 which is readily rocked by some suitableelement of the machine, as, for example, by a portion of the driving gear for the feed mechanism C, as'will be pointed out more full hereinafteni The hopper D being intended for use with the three passage valve 40 is divided by partitions I03 into compartments I04 which communicate directly with the passages 38 of the. valve mechanism. The sheet metal construction just described is connected to a basic casting I05 which has similar passages I08. The latter are separated by partitions I01. such that the compartments I04 and passages I08 and 38 are in each case in communication with each other, there being three such in the present embodiment. The basic casting I05 is provided I with a lower face which rests upon and is secured to a peripheral flange I08 upon the casing member 24 of the valve structure. The connection is preferably made by bolts I09 which pass through openings in the flange I 08 into threaded engagement with the casting I05, all as clearly shown.

The agitator within the hopper may take different forms. A suitable type is illustrated in United States Patent No. 1,476,996, granted December I1, 1933. Another simple form is illustrated in the drawings, particularly in Fig. 1. As there shown, the lever I00 is secured to a transverse shaft IIO suitably journaled in bearings located at the upper edges of the side walls 89 and 90 of the hopper. The shaft IIO carries arms III, at least one for each compartment I04 of the hopper. Each arm carries a plunger rod II2 terminating in' a plunger head 2* which'is carried up'and forced down in the commodity and so keeps it agitated and free to be fed through the passages I05 and 38 to the guiding valve 40 of the mechanism C. Guide rods II2 pass through openings in the plate or head H2" and are held in fixed position in the hopper compartment by being fixed to a portion of the hopper construction. The head H2 in each case, there being at least one for each hopper compartment, moves freely up and down along theguide rods. The rods will be inclined to suit theinclination of the hopper compartment in which it is located.

' The table mechanism E includes a supporting The arrangement is frame 3' which is mounted on the forward side of the mainframe B. The connection between the frame 3 and frame B is an adjustable one, preferably provided by cooperatingtongues and grooves. In the embodiment illustrated the frame B is provided with vertical tongues II4 which cooperate with vertical grooves H5 in the frame I I3. Preferably the tongue and groove arrangement is a dove-tailed arrangement or its equivalent. In the present instance the outer edge of each tongue I I4 has a laterally projecting flange which also lies within the groove H5. Overhanging this flange is a strip H6 secured to frame 3 along the edge of the groove by any suitable means, as the screws III. In this way the tongue H4 is locked within the groove I I5 but is capable of vertical movement relative to it. Thus the front frame II3 may be readily adjusted in a vertical direction on the main frame B.

The frame I I3 is provided with a bearing yoke 6* having a bearing at each end for the vertical stem or post III which pivotally supports v secured to the cam shaft R. The cam I25 is provided with a peripheral groove I28 into which the rollers I24 are adapted to extend. The space between these rollers, as clearly shown in Fig. 6, is Just sufllcient to nicely embrace the cam projection I21 which lies between the overlapping portions of the spiral groove I28. The cam faces are such that as the shaft R'is rotated. they will -contact with the rollers I24 and quickly advance the table I I8 through the space of one step. Following this there will be a period of rest, and, then, as the cam again reaches its actuating position, the table II8 will be given another forward step. In this way the table 8 is advanced intermittently with a rest period following each step. The cam shaft R is suitably journaled in bearings I28, I29 provided on the under side of the yoke frame 6'. Between the casting H9 and the member H8, a ball bearing I3I may be located so as to facilitate the travel of the table II8 about its non-rotary pivot III In order to be able to rotate the shaft R by hand for the purpose of adjusting the position of the table II8 without starting the driving motor I, the shaft R isprovided with a hand wheel I30.

The pivotal supporting shaft Ill, although not rotatable may be raised and lowered for the purpose of adjusting the height of the auxiliary frame H3 and the table II8 which it carries. This is brought about through the agency of a bracket I32 secured in any suitable way, as by bolts I33, to one of the walls of the base A. The bracket I32 provides a bearing I34 for the lower end of the post II'I. There is also an arm I35 which is apertured to allow for the passage of the post Ill! and this arm is secured to an upright I36 upon the bracket I32 by suitable means, such as a bolt I31, and provides a space between it and the upper side of the bearing I34 for a nut I38 which has threaded engagement with the threads upon the lower end of the post Ill. The periphery of the nut. I38 is provided with beveled way the containers P carried in the different openings I40 of the table I I8 are nicely positioned with reference to the outlet 43 of the valve mechanism C. Different ways of rotating the nut I38 may be employed. In the present instance the arm I35 is provided with a boss I4I on its under side'and the boss embraces the post III but is I not in threaded engagement with it. A small opening in the face of the boss I4I permits the insertion of the end of a crank I42 and a beveled gear I43 on the crank I42 engages the teeth of the beveled gear I39 when the parts are thus assembled. The crank I42 may then be turned by hand and the result will be a rotation of the nut I38 either to raise or lower the shaft Ill and its supported elements. The tongues H4 and grooves II5 maintain the frame I33 in proper alinement and. in firm connection with the frame B. This table mechanism E thus carries cartons or other containers step by step around with its table II8. Where automatic feeding and capping are employed the containers P are dropped from the feeder into the openings I40 as they appear in the container feeding position, designated a, in Fig. 6. The containers are fed one by one into the openings I40 as they appear at this position. Then two advance steps of the table IE8 carry each container from the feeding point a to the filling position I) located directly beneath the spout or outlet 43 of the measuring mecha nism C. Two more steps will advance the filled container to the capping position '0. Again two more steps will bring the container to the ejecting position d. From the latter position each filled and capped container is ejected by the mechanism I into the chute H as previously mentioned. When each container comes into the filling position b, it is given an upward movement so as to force its upper end into contact with the lower end of the outlet 43 of the valve mechanism. In other words, at the time of filling, the cup or other container is shoved up against the under side of the spout of the valve. This action is brought about by certain mechanism associated with the table mechanism E. In the em bodiment illustrated the lower end of the carton is pressed upward by a double or looped arm I44 extending laterally from a small casting I45 secured to the upper end of a pin or rod I46 mounted for vertical movement in a bearing formed in a portion I4I of the frame structure. Vertical movement is given to these parts by an actuating lever I48 fulcrumed to a fixed part of the machine at I49 and bearing at one end an anti-friction roller I56 which is adapted to engage with a cam I5I on the cam shaft R. The end of the lever I43 which is adjacent to the vertically movable pin I46 is provided with a yoke I52 which forms part of a universal joint connection with the lower end of the pin I46. The yoke is connected by a horizontal pivot pin I53 to a block I54 which is free to rotate upon the sleeve I51 upon the pin I46. A collar I55 is secured to the upper portion of the sleeve I5'I by a pin I58 or like means and serves to limit the upward movement of the block I54 upon the sleeve I51.

A knurled head I56 formed at the lower end of the sleeve I51 bears against the under side of the.

block I54 to limit its downward movement, the head I56 engaging the block I54 and holding it up against the collar I55. The interior of the sleeve I5! is threaded and so is the lower end of the rod I46. As a result of the threaded engagement of these parts, the block I51 may'be adjusted up and down upon the rod I46 to give proper vertical adjustments to the container engaging arm I44.

The carton feed mechanism may vary greatly in construction. Indeed, the machine is designed so that different container feeders may be used upon the machine with satisfaction. Thus the bracket I60 shown at the left in Fig. 6 provides the usual support for the container feeder whatever its construction; The container feeder F is merely illustrative. In general, in feeders of this kind, it is only necessary to employ a magazine I6I for the containers P and in association with it some suitable reciprocating mechanism I62 for separating the lowermost container of a stack of containers and allowing it to drop into the positioned opening I40 in the table mechanism E. Inasmuch as the container feeder in itself forms no part of the present invention it will sufiice to point out these essentials of the feeder mechanism and show how the machine, as disclosed, provides for the actuation of the reciprocating member of the feeder. In the present instance the main supporting bracket I63 of the feeder is secured at its lower end to the bracket I60 and the guideway I64 for the slide I62 is properly supported at the upper end of the bracket I63, all as particularly illustrated in Fig. 1.

In like manner the capping mechanism G may be variously constructed Indeed-the design is such that different makes of cappers may be used upon the machine with satisfaction. The bracket I64 supports the capper G. The latter requires a magazine I65 for the caps I66 and, ,in association with the magazine a suitable reciprocating member I61 which travels to and fro in a guideway I6! and operates to pick oif the lowermost cap and advance it to a position wherein it will be shoved downward by a plunger mechanism I69 into its final position in the top of the container. Since the cap advancing and plunger applying movements are the only movements required it will be obvious that the different mechanisms of different types of cappers may be readily actuated by the actuating mechanisms illus trated. In the present case the reciprocating mechanism I6I which picks off the lowermost cap is actuated by means of a reciprocating rod or link I69. In like manner a centrally pivoted lever I10 is actuated through a connecting rod III to give the plunger movements required.

By way of further disclosure of suitable feeder and capper mechanisms for use in association with the other mechanisms of the machine, attention is called to the following United States Patents, viz:

1,171,996, Wilkinson, granted February 15, 1916.

1,260,432, Nias, granted March 26, 1918.

1,403,941, Cundall, granted January 17, 1922.

1,913,743, Borchert, granted June 13, 1933.

The chute H is of simple construction and need not be especially described. It will suffice to say that the same is preferably composed of metal and has side walls and is supported in inclined position with its upper end adjacent to the discharge position If at which position the filled and capped containers are ejected. These filled and capped containers enter the upper end of the chute and travel down the same to be further handled as may be necessary.

The ejector mechanism I comprises a headed rod I12 which is reciprocated vertically at suited timed intervals to engage the bottom of a container P in the position d of Fig. 6 to push it up out of the Opening I48 in which it has rested during its travel from the feeding position a, wherein it was initially deposited upon the table I18. This upward movement and the pressure behind it are sufflcient to dislodge the filled and capped container from its seat in the table and to tumble it into the chute H.

The rod I12 is provided with guide bearings I13, I14 in a bracket I15 secured to the forward edge of the frame H3. The rod is movable vertically and operates during rest periods in the travel of the table II8 to pass its head I18 upward, and then downward, through each opening M8 as it presents itself in the delivery position d of Fig. 6. A block I11 is secured to the rod I12 near its lower end. This block is pivotally connected to the lower end of a link I18 which is pivoted in turn at its upper end to the long arm of a bell crank lever I19 pivoted to a lower portion of the bracket I15. The short arm of the bell crank lever I19 is provided with a slot I88 which cooperates with a pin I8I which is fixed to and extends outward from one end of a slide bar I82 which is adapted to move to and fro in a direction substantially parallel to the cam shaft R and a short distance forward of it. Suitable guides I83, I84 for the actuating bar I82 are provided near the forward edge of the frame I I3. The end of the bar I82 distant from the bell crank lever I19 is provided with a laterally projecting pin I85 carrying a cam roller I86 which rides upon the cam edge I81 of an annular cam i138 mounted upon and secured to the cam shaft R. The same end of the bar I82 carries a hook I89 for receiving one end of a coiled retractile spring I98 which extends lengthwise of the bar I82 and is secured at its distant and to the pivot pin I9I of the bell crank lever I19. The spring I98 holds the cam roller I86 up against the cam face I81 at all times. Consequently, the actuating bar i82 moves back and forth as the cam 888 rotates. The cam face I81 is such that there is one complete to and fro reciprocation of the bar I82 for each rotation of the shaft R, with a rest interval before each to and fro reciprocation is begun. As the bar I82 is reciprocated, the bell crank lever I19 is rocked and the ejector head I16 is moved up and down through a complete cycle. In its upward movement, it strikes against a filled container P, if one is in position, and carries it upward beyond the table I I8 out of the opening I48 in which it had rested and directs it laterally into the upper end of the chute H. If no container is in the opening which presents itself then the ejector passes up and down without performing any ejecting function. A distinct tilt is given the filled and capped container toward the chute by having the head I18 strike the under side of the container a little toward the center of the table 8 from the exact center of the container bottom. The action of the ejector upon the container to hold it against a too rapid tilting toward the chute is provided by giving the head I16 a forwardly projecting loop I92 which also engages the bottom of the container during the ejecting operations.

Having gone over the diiferent mechanisms the machine and having considered their parts and relative operations, it may be well now to consider the trains of gearing and other elements which bring about the operations of the various mechanisms from the source of driving power.

To begin with, the motor M is preferably located within the base A and is secured to the under side of a hanger I96. The latter is in the form of a slab or plate and is pivoted to lugs 691 secured to the inside of one wall of the frame A. The opposite end of the hanger I98 is apertured for the passage of a rod I98, and a nut I99 is threaded on the lower end of the rod 198 and positions the rod with reference tothe hanger. The downward movement of the rod I98 is limited is by. a collar 288 which is secured by any suitable means, as a set screw 28I, to the rod I98 and the collar 288 engages the upper surface of the top 282 of the frame B to limit the downward movement of the rod. A hand wheel 283 is likewise secured to the upper end of the rod I98. The rod also passes in threaded engagement through a threaded portion 286 of the bottom of the main frame B. with this construction it will be seen that as the rod I88 is rotated it will be raised and lowered within the limits permitted by the end of the hanger I96 and the collar 280, to move the plate or hanger I96 up and down about its pivotal point. In this way the position of the motor may be changed in elevation, as desired, within certain limits.

The armature shaft 281 of the motor M, which is preferably an electric motor of suitable design for the purpose, is provided with an expansible pulley 288. This pulley is of well known contruction and includes two parts which may be easily forced apart in opposition to the pressure of a compression spring 288 acting between one of the members of the pulley and a stop member 2| 8, such as a washer or the like, secured to the pulley shaft by a nut 2 or other means. These pulleys are well known and form no part of the Present invention. Illustrations of them will be found in the following patents:

986,303, Borlase, granted August 2, 1910.

1,350,670, Ritter, granted August 24, 1920.

1,662,654, Abbott. granted March 13, 1928.

With this kind of pulley 288 it is possible to lower the speed of the gearing driven by the motor by simply forcing the pulley members apart slightly and decreasing the effective diameter.- Allowing the pulley members to approach each other produces the opposite result, namely an increase in speed. Because of the weight of the motor M it will be obvious that when the hand wheel 283 is turned so as to drop the motor then the effective diameter of the pulley engaged by the belt 2I2 is decreased and with a constant speed motorthe speed of the pulley 2| 3 driven by the belt 2 I2 will be reduced with a corresponding speed reduction in other parts of the gear train. On the other hand, if the motor be raised, then the effective diameter of the pulley 288 will be increased and the speed of the pulley 2|: increased.

The pulley 2I8 is mounted upon a transverse shaft 2 I4 and secured to the same by a transverse pin 2I5 or the equivalent and the shaft 2 is journaled in bearings 2I8 and 2" formed in portions of the upper part of the main frame B. 70 The shaft 2 carries a pinion 2I8 which meshes with the gear wheel 2I9 mounted to rotate about the axis of a transverse shaft 228. The shaft 2281s not driven at all times by the wheel 2I9 but is driven only when the clutch N operates to 75 connect these two elements. In the particular clutch employed, which is of the pin type, the ear wheel 2l9 has a large central bore which fits over and travels upon the peripheral surface of the crank disk Q, indicated at the point 22| in Fig. 6. The disk Q is keyed or otherwise secured to the stud shaft 229 which shaft extends forward from the bearing 222 formed in the rear wall of the frame B and carries the crank space for a torsion spring 229. The latter is secured at one end by thrusting the end of the spring into a small opening 239 formed in an adjacent shoulder of the pin. The other end of the spring is similarly held in a hole 23! provided in the casing 221, as most clearly illustrated in Fig. 6. The spring 229 tends to hold the pin 223 with its slot 232 extending radially of the crank disk Q. When thus extended the wall 233 forming the bottom of the slot 232 engages with one or other of the clutch plates 234 secured to the gear wheel 2 I9. This is the normal position of the parts and the position in which the crank disk Q and driving gear wheel 2l9 are clutched together. This is the position in which the spring 229 normally holds the parts. When it is necessary to disconnect the crank disk from the driving gear wheel 2 l 9, then the pin 223 must be rotated from its normal positionand rotated against the torsional pull of the spring 229, until its wall 233 lies circumferentially with reference to the crank disk Q. When this position is taken, the projecting clutch members 234 upon the gear Wheel 2l9 will pass freely through the slot 232 and will not operatively engage the pin or any part of it to drive the crank disk. This movement out of the normal spring retained position is brought about by actuating a nub or projection 235 secured to or forming an integral part of the pin 223.

Passing for the moment a consideration of the control mechanism for bringing about this unclutching movement of the clutch pin, it may be assumed that the parts are in clutching position and the balance of the gear train brought into play by the clutch considered. As soon as the crank disk Q is rotated, it carries around its crank pin 236 with resulting operations of the commodity filling mechanism C. The first of these movements which may be considered is the oscillating movement of the valve 49. As previously pointed out, this valve is oscillated to and fro between its stops 16 by the link 66. The latter has a slot 231 through which the crank pin 236 extends. The result is that as the crank disk Q rotates in the direction of the arrow as shown in Fig. 3, there are intermittent oscillations of the valve 49, the valve being moved to and fro by the thrust and tension action of the link 66 occurring when the pin 236 engages the opposite ends of the slot walls and the intervening rest periods occurring while the pin is traveling within the slot.

The same rotation of the crank disk Q actuates similar but oppositely disposed connecting rods each of which includes an outer portion 238 and an inner portion 239. The inner portion 239 of each pin is journaled on the crank pin 236 and at its outer end it-is bored out and threadedv to receive the inner threaded end of the rod 238 which formsrthe outer portion of the connecting rod. At its outer end each extension rod 238 carries a knurled head or block 249 which is fixed to the rod in any suitable way as by a pin 24!. Inward of the head 249 is a guard 242 which resembles a washer. occupies a position on the rod 239 just inward of the guard 242. This block is also preferably fixed to the rod 238 as by a pin 244. The spaces between the blocks 243 on the one hand and the outer ends of the connecting rod members 239 provide travel-ways for the blocks 245. The latter are pivotally secured to the lower ends of levers 246, 241 which in turn are pivotally connected at their upper ends to the piston rods 36 and 31 respectively. These levers 246, 241 are pivoted at intermediate points to brackets 248 and 249 respectively. These brackets extend outwardly from adjacent portions of the main frame B.

It may be noted at this point that the lever 246 is formed integral with and virtually is part of the rocker arm I92, previously referred to, by which the connecting rod [9i and associated agitator mechanism in the hopper D are operated. Each time the lever 246 is rocked through the action of the crank pin 236 and associated connecting rod (made up of the parts 238, 239), the agitator is moved up and down, or otherwise as the case may be, depending upon the type of agitator employed.

In operation it will be seen that as the crank shaft rotates, the pistons 34, 35 and the intervening directing valve 49 operate in timed relation to'bring about proper fillings of the measuring cylinders followed by discharges from the same into the positioned containers. The lost motions provided, in the case of the valve 49 by the pin 236 cooperating with the slot 231, and provided,

in the case of the pistons 34, 35 by the blocks having a free travel upon the connecting rod extensions 238, give the necessary timed relation between the filling and discharge operations of the pistons and valve of the measuring mechanism C.

The lost motions provided by the travel-ways for the blocks 245 upon the rods 238 may be varied at will tovary the measure of the commodity taken up by the respective measuring cylinders. This variation in the case of each set of cylinders, 32 or 33 as the case may be, is provided by adjusting the outer portion 239 of the connecting rod relative to its inner portion 239. This is done by the operator grasping the appropriate knurled head 249 and turning the corresponding rod 238 into or out of the part 239 as may be required to lengthen or shorten the stroke of the pistons, 34 or 35, to vary the measure of the charge of commodity taken from the supply. The guard 242 protects the fingers of the operator from being injured by the block 245 when adjustment is made without stopping the machine.

In connection with the operation of the pistons 34, 35 and the valve 49., it should be noted that the valve 49, when at rest, occupies either the position of Fig. 3 with the dividing partition 59 extending upward toward the left or the position of Fig. 9 with the same partition extending upward toward the right. It oscillates between these positions and between the travel periods there are rest periods. These rest periods occur while the crank pin 236 traverses its slot 231,

Another block 243 first in one direction and then in the other. While the valve is traveling the pistons 34, 35 are at rest due to the blocks 245 passing along the travel-ways upon the rods 236. On the other hand while the valve 40 is at rest the pistons 34.,

35 travel first to the right and then to the leftas the parts are viewed in Figs. 3 and 9. Thus, In the rotation of the crank pin 236, there are .four periods corresponding to four quadrants on the disk Q. While the pin 236 traverses one quadrant, which we may call the first, the valve 40 remains at rest in, say, the position of Fig. 9, and the pistons 34, 35 move to the left as shown in that figure, the pistons as there shown being ready to begin their stroke to the left to discharge cylinders 33 and fill cylinders 32. During the next quadrant, the second, the valve 40 is moved to the position of Fig. 3 and the pistons 34, 35 remain at rest, the parts being shown at the beginning of the quadrant period. During the traverse of the third quadrant by crank pin 236, the valve 40 remains quiescent and the pistons 34, 35 move to the right, thereby emptying cylinders 32 and filling cylinders 33. The fourth quadrant brings a movement of the valve 40 back to the first position considered while the pistons remain quiet. Thus, there are alternations in the operations of the valve and pistons and through two positions for each.

The control mechanism 0 brings about an operation of the clutch Nin response to conditions present upon the container carrying table H8 of the table, mechanism E. Normally containers are fed at regular intervals into the openings I 40 of the table and there is no reason for stopping the regular operations of the filling mechanism C. However, should it happen that an opening I 40 presents itself at the filling position b (Fig. 6) without a container in it, then provision must be made to prevent the operation of the filling mechanism C. The control mechanism O performs this function. When the containers appear regularly the clutch N remains in clutching position and the parts move continuously without interruption. However, when an opening I40 appears without a container in it, then the mechanism 0 operates to throw the clutch into unclutching position. This allows the parts of the mechanism C to stop during the travel of the table through another step. If, again, the opening I40 is devoid of a container, the unclutching condition continues for another step. Finally when a properly filled opening I40 presents itself, the clutch is thrown to its clutching position and the filling operations continue.

As previously pointed out, the clutch pin 223 occupies two positions. In one of these the face 233 is practically tangent to the periphery of the crank disc Q. and in the other position it is shifted into a substantially radial position, wherein it engages one or other of the clutch plates 234. The coiled torsion spring 229 which surrounds the clutch pin 223 tends to hold the face 233 of the pin in the clutch engaging position. This means that the projection 235 at the end of the pin occupies the position of Fig. 5 when the pin is not interfered with by anything extraneous to 'the clutch itself. In other words, when unrestrained the torsion spring 229 tends to hold the projection 235 in the position shown in Fig. 5, which is the clutch engaging position.

For the purpose of moving the projection 235 into the unclutching position, wherein the wall 233 at the bottom of the channel 232 lies in its tangential position, there is provided a yoke-like frame 252 having upwardly extending arms pro vided with anti-friction rollers 253. The frame 252 is provided with downwardly extending lugs 254 through which pivot pins 255 extend. The latter are threaded through threaded openings in portions of the lower part of the main frame B. Lock nuts 256 on the pins 255 serve to hold them in adjusted positions. At one end the frame 252 is provided with a crank arm 251 and the outer end of this crank arm is connected by a rod 250 to an intermediate point in a pedal lever 259, the lower end of the rod extending through an opening in an angular projection 260 carried by the lever 259. The lever 259 is pivoted to projections 26I extending inward from the base A at a point adjacent to its rearmost foot 20. The forward end of the lever 259 is provided with a flattened portion 262 for the foot of the operator to engage when he wishes to press the lever downward. The lever 250 is normally held in its uppermost position by a spring 263 which is secured at one end to the lever and at the other end to a horizontal portion 264 of the base A. Adjusting nuts 265 serve to determine the throw of the frame 252 under normal pedal depression. The downward movement of the pedal may be limited in any desired way and in the present instance is movable until it comes in contact with the floor which serves as a stop to limit its downward movement. The frame 252 is additionally yieldingly held in nub-engaging position by a coiled tension spring 266 which is secured at one end to the crank arm 251 and at its other end to a fixed part of the frame B. The nub-engaging position of the frame 252 is that position which it occupies when its anti-friction rollers 253 are up near the face of the crank disk Q and in position to engage the nub or projection 235 on the clutch pin.

As before explained, if the rollers 253 are positioned close to the face of the cam disk Q then the clutch pin will be thrown to non-engaging position and the driving shaft 220 will be stopped until the frame 252 is moved away from its position close to the face of the crank disk. When in this outer position, the rollers 253 are not in the path of travel of the nub 235 upon the clutch pin, and consequently the crank disk and driving gear wheel 2I9 remain in clutched position and therefore move together as a unit.

When it is desired to run the machine continuously without having cartons in the openings I40 of table H8, then it is only necessary to press down upon the pedal lever 259 and thus keep the rollers 253 out of possible engagement with the projection 235 on the clutch pin. This will leave the pin free to act under its spring force and hold the parts in clutched engagement. However, when containers are being fed to the table mechanism then the foot may be removed from the pedal 259 and the mechanism will operate entirely under the control of the control mechanism O.

In considering this mechanism 0, it will be noted that it extends in its operations from the table II8 to the clutch mechanism N. Adjacent to the table H8 is a vertical rock shaft 210 suitably journaled in portions 21I and 212 of the main frame B. At the upper end of this rock shaft 210 is a bearing block 213 which carries a laterally projecting pivot pin 214. The pivotpin 214 carries a floating feeler arm 215 and a pin engaging arm 216. The arm 215 extends at its free end over the edge of the table H8 and carries on its under side a plate 211. The arm'216 extends at its free end below the table I I6 and in its uppermost position is operative to engage downwardly projecting pins 218 on the under side of the table near its periphery. The arrangement is such that the arms 215 and 216 move together, being both connected together and pivoted on the same pivot pin 214. The arms 215 and 216 together with the plate 211 are counterbalanced to a limited extent by the weight 219 located to the right of the pivot pin 214, as the parts are viewedin Fig. 13. The weights of these parts, however, are such that the weight of the parts to the left of the pivot pin slightly exceeds that of the weight to the right, as the same are viewed in Fig. 13. The counterbalance provided by the weight 219 thus prevents the possibility of the plate 211 pressing too heavily upon the containers P in the openings M as they present themselves beneath the plate. In other words, by counterbalancing in this way, the pressure upon .the containers is very light and yet there is sufiicient movement of the parts to cause the arm 216 to engage the pins 218 whenever containers are in position and to allow the arm 216 to miss the lower ends of the pins 218 when containers are not in position.

It will be seen that when a container P is presented to the plate 211, the latter will be moved upward with a corresponding elevation of the pin actuated arm 216. As the latter is actuated by a pin 218, the rock shaft 210 is rocked so as to move the clutch control rollers 253 out of the path of travel of the clutch pin nub 235. This transfer of motion is brought about by a rock arm 28l secured to a lower portion of the shaft 218 and acting through a link 282 and a crank arm 283 to oscillate a frame 286 supported by the frame 252 and carried by vertical pivot pins 285, 286. The oscillatory frame 282 carries a roller 281 at its upper end and this roller cooperates with a cam 288 located on the face of the gear wheel 219. The various parts in this train of connections are normally held in position to cause the filler arms 216 to engage the control pins 218 whenever the arm 216 is properly elevated and at the same time to yieldingly maintain the vertically pivoted frame 286 with its roller 286 out of the path of travel of the cam 288. This is done by means of a coiled tension spring 229 which is connected at one end to a crank arm 290 associated with the rock shaft 210 and at the other end to a fixed portion 29! of the main frame B of the machine.

The frames 252 and 281 have a cooperating relation. Whenever the frame 282 is in its normal position, its roller 281 will not engage the cam 288, as'already explained. However, when the control mechanism is actuated so as to throw the member 284 against the action of its spring far enough to bring its roller 281 into the path of travel of the cam 288, then the action of the cam upon the roller will press the frame 282 and with it the frame 252 outward away from the face of the crank disk Q.

The operation thus brought about through the action of the control mechanism 0 is the same in ultimate effect as if the pedal 259 were operated and the frame252 thrown outward away from the disk face as before explained. This time, however, the action has been caused by the presence of a container in an opening 140 in the rotary table H8. Since the frame 252 is thrown outward, the clutch pin will remain with its nub 235 in the position of Fig. and a unitary rotation of the driving gear wheel 218 and the clutch disk and shaft 220 will occur. This action will bring about a proper operation of the filling mechanism C when the container which causes the operation of the control mechanism 0 is in position to receive its charge of commodity.

Obviously, if a container is not present in an opening 0, the levers 215 and 216 will remain in their lowermost positions and there will not be an engagement of the arm 215 with a pin 218, and, consequently, there will be no rocking of the shaft 210 with the resulting movement of the clutch controlled rollers 253 away from the face of the crank'disk Q. Therefore, in such case, the nub 235 will be rocked to the full line position of Fig. 5 and the face 233 of the pin will slip over the edge of the disk Q and there will be no driving of the latter by the driving gear wheel 219. This, of course, means that there will be no actuation of the filling mechanism C at a time corresponding to the presenting of the opening 0 at the filling position b.

Thus, it will be seen that during the continued operation, where proper containers successively present themselves, there will be intermittent actuations of the control mechanism 0, one actuation for each container, and the clutch will remain in clutching position. In contrast to this, if an unoccupied opening presents itself, then there will be a corresponding failure of the mechanism O to operate and a corresponding cessation of the operation of the filling mechanism 0. Thus, the filling of the containers is placed under the control of the containers themselves. And, yet, if desired, the machine may be advanced through any number of steps by use of the pedal mechanism even though containers are absent from the table.

Turning now to the train of gearing by which the cam shaft R. is operated it will be seen that the shaft 2141, which is driven directly from the motor M through the agency of the belt 212 and the pulleys 208 and 212, is provided with a sprocket wheel 2% which is employed to drive a sprocket wheel 2% through the agency of a sprocket chain 296. The sprocket wheel 295 is carried upon the outer end of a worm shaft 291 mounted within a gear box 298 suitably supported by a bracket 292 secured to a portion of the main frame B. The worm shaft 291 is provided with a worm gear wheel 300 which meshes with a gear wheel 300 positioned at right angles to the wheel 300 upon a transverse shaft 300, which carries at its outer end a sprocket wheel 301. The worm shaft 291 and worm wheels 300 an 301i form within the box 292 a gearing by which the direction of travel is changed 90 degrees. In this way the sprocket chain 302 travels in a plane at right angles to that in which the chain 296 travels, and is in position to engage a sprocket wheel 5303 upon the end of the cam shaft R, as clearly illustrated. The sprocket chain 302 has one stretch which engages with a guide sprocket wheel 302 journaled in suitable bearings carried by the vertically adjustable table frame 1 I3. The other stretch of the sprocket chain 302 similarly engages a sprocket wheel 306, which is carried at one end of a lever 301. The latter is intermediately pivoted to a bracket 218, also carried by the table supporting frame H3. The end of the lever 301 distant from the sprocket wheel 306. is constantly drawn upon by a coiled tension spring 309 which is secured at one end to the lever 301 and at its other end to a fixed point of the frame 113. The two sprocket wheels 304 and 306 together with the yielding mounting of the latter constitute a belt tightener for the sprocket chain 302 and by reason of its belt tightener action,

proper tension is maintained in the chain at all times for transmission of power to the cam shaft R whatever the vertical adjustment of the table supporting frame II3 may be, and, indeed, the same will continue even while the table supporting frame is being adjusted.

As previously pointed out the cam shaft R is provided with the cam I88 having a peripheral cam face or edge I81 which cooperates with a cam roller I86 to bring about vertical actuations of the ejector mechanism 1. This same cam face I81 also cooperates with a-cam roller 3l2 rotatably mounted on the lower end of a lever 3I3. The latter is pivoted at an intermediate point to a supporting web 3I4 which extends outward from the bracket or frame I63 of the feeder F. The upper end of the lever 3I3 is connected with the outer end of the reciprocating feed member I62 by a pin and slot connection, shown most clearly in Fig. 14. Normally the roller 3I2 rides on the cam edge I81 and is held in close contact with the same by a coiled tension spring 3!!) which is secured at one end to the lever 3i 3 adjacent to the roller 3I2 and at its opposite end to some relatively fixed part of the machine. As the shaft R rotates the lever 3I3 oscillates, there being one complete to and fro reciprocation of the lever for each revolution of the shaft. Each such to and fro movement of the lever 313 gives the feeding member I62 a forward and return. stroke to feed one of the containers to the table II8.

When it is desired to stop the feeder it is only necessary to hold the roller 3I2 away from the cam face I81. This is preferably done by employing a hook 3I1 pivoted to the web 3I4 so that its hooked end may engage a pin 3I8 on the upper portion of the lever 3 I3 as clearly illustrated. As long as the hook 3I1 operatively engages the pin 3I8 the feeder will be held inactive. In order to easily manipulate the hook 3I1, that is to say, to lift it out of its position of operative engagement with the pin 3I8 on the one hand and on the other hand to allow it to drop into said position under its own weight, a cam bar or rod 3I9 may be employed. This bar is mounted for frictional rotation in the web 3I4. By its frictional engagement with its bearing the rod may be easily rotated to any desired position and when rotated to such position it will be held there by the frictional contact of the parts. The bar 3!!) is provided with a projection 320 which operates to engage the under side of the hook 3I1 to raise the latter above its position of engagement with the pin 3I8. It will be noted that the pivotal axis of the hook 3I1 is adjacent to the axis of the cam bar 3I9. This brings about the proper actuation of the hook into engaging and non-engaging positions in re-- sponse to the rotations of the bar 3I9 Instead of employing the projection 320, obviously the bar might be otherwise shaped or equipped so as to give the necessary movements to the hook when the bar is rotated. As long as the bar 3I9 remains in that position which holds the hook 3I1 elevated, the feeder F will be operated. As soon as the bar 3I9 is rotated so as to allow the hook 3I1 to operatively engage the pin 3I8, then the roller 3! 2 will be held out of engage.- ment with its cam face and the operations of the feeder will be discontinued.

When it comes to the capper G then two movements must be communicated to its parts, one to the cap shifting member I61 and the other to the plunger I68. These movements are brought about through the agency of a cam 323 upon the cam shaft R, the cam 323 being quite similar to cam I88 just referred to in connection with the operations of the feeder. The capper cam 323 has a cam face or edge 324 which cooperates with two cam rollers 325 and 326 to bring about two required movements of the capper parts. v

The cap fe'ed member I61, as before noted, is reciprocated by the connecting rod or link I63. This link is pivotally connected at its inner end to the upper end of a lever 321 which carries the cam roller 326 at its lower end and is pivoted at an intermediate point to the frame 328 of the capper G. It will be seen by reference to the shape of the cam edge 324 that there is one complete reciprocation of the cap feeding member I61 for each complete rotation of the cam shaft R. This reciprocation removes a cap from the lower end of the stack in the capper magazine I65 and shifts it into position to be actuated by the plunger I68. The shape of the cam face 324 is such that the cam rollers 325 and 326 operate alternately to bring about their respective movements. Consequently the plunger I68 will not operate until after the capper feed has operated and properly placed a cap in possition for application to the container. Generally speaking, while the plunger I68 is inactive the feed member I61 is active to advance a cap and while the feed member I61 is inactive the plunger I68 is active to apply the cap to the container.

The cam roller 325, which is employed in actuating the plunger I68, is connected to the lower end of a bell crank lever 323 which is pivoted to the frame 323. The short arm of the bell crank lever is pivotally connected at its outer end to the lower end of the actuating link I1I which, as previously pointed out, rocks the lever I10 to bring about the operation of the plunger I68. In this connection it may be noted that the lever I10 is pivotally mounted upon the upper end of a supporting arm 330 which is pivoted at its lower end to a portion of the frame 328 of the capper. The supporting link 330 provides a shifting fulcrum for the lever I16 so as to permit a proper lineal movement of the plunger I68 as the latter is actuated to apply the cap to the container.

The bell crank lever 329 is mounted on a pivot 33! carried by the frame 328 and the pivot 33I also carries an arm 332 which is either integral with the bell crank lever 329 or secured so as to move with it. The outer end of the arm 332 has a spring 333 connected to it. The spring 333 is a coiled tension spring which is connected at its upper end to the arm 332 and at its lower end to an angular extension 334 at the lower end of a supporting rod 335. which is mounted at its upper end in the frame B of the machine, the particular connection being made by securing the upper end of the rod to a boss 336 extending downward from a flange 331 of the frame B. The spring 333 is normally undertension and by reason of the connections justnoted, causes the cam roller 325 to engage its cam face 334 during the rotation of the cam shaft R.

The roller 326 is maintained in contact with the same cam surface 324 by a practically duplicate arrangement. The lever 321 is provided with an arm 346 which moves in a planeparallel to the plane of movement of the arm 322. The outer end of the arm 346 is provided with a coiled tension spring 34I which extends downward which is adapted to engage a shoulder 343 upon a pivoted latch arm 344. The latter is pivoted to one side of the capper frame 328 and normally the shoulder 343 lies below the path of travel of the pin 342 and does not interfere with the operation of the mechanism. However, when it is desired to stop the feeding of caps, the latch arm 344 is drawn upward and the shoulder 343 slipped in behind the pin 342 at the time when the cam roller 326 is at its outermost position. While the latch arm 344 maintains this inoperative relation, the reciprocating member I61 is quiescent, consequently no caps are fed forward.

In the present instance, no provision is made for holding the cam roller 325 out of engagement with its cam face 324, and consequently the plunger I68 continues to move up and down, but, inasmuch as no caps are presented when the latch 344 is operating to hold the feeder bar I61 out of operation, no caps are forced into containers. In other words, so long as the caps are not fed forward to the plunger position, there is no need of stopping the plunger action, since in any event, no caps can be applied.

In order to properly position the rotary table II8 of the mechanism E relative to the feeder position a, the filling position b, the capping position c and the discharge position d, we provide means for adjusting the position of the actuating drum cam I25 upon the cam shaft R. The cam I25 is splined or otherwise mounted upon the shaft B. so as to rotate with it but at the same time be free for a certain amount of longitudinal movement along the shaft. which will be properly secured to the shaft R and movable in a key-way in the bore of the cam I25, will provide for such relative movement of the parts. Since the cam surface I25 of the cam I25 cooperates with the cam rollers I24 positioned on the under side of the table IIB, it is possible by shifting the cam I25 along the shaft R, to accurately adjust the table circumferentially with reference to the various positions a, b, c and (1 previously mentioned. To bring about this indexing adjustment we preferably providean adjusting screw 348 which passes freely through a bore in the cam member I5I, which is fixed to the shaft R, and into threaded engagement with a threaded bore in the adjacent portion of the cam I25. A head 349 at the end of the threaded pin provides for the rotation of the pin by a wrench so as to screw it into or out of the threaded opening in the cam I25. When the proper setting is obtained then the parts are held in position by a lock nut 359. Obviously other ways of arranging this threaded adjusting pin 348 and its associated parts might be employed and the same adjustability obtained. It will be noted that. it is because of the quite accurate fit of the cam rollers I24 within the slot I26 of the cam I25 that it is possible to quite accurately adjust the position of the table H3 by shifting the position of the cam I25 longitudinally of the cam shaft R.

Obviously, in building the machine various parts may be protected by coverings or casings such as the casing 353, shown in Fig. 1, which A key or feather 341I,

incloses some of the reciprocating parts at the front of the machine, the same serving also as guards for the protection of the user of the machine. It will also be obvious that the circuit of the electric motor M may be controlled by a suitable switch located at a convenient point. As illustrated in Fig. 1, such a switch, designated 354, is located on the front of the machine just above the chute H and adjacent to the capper G and the electrical connections from it to'the motor extend through a conduit 355 shown passing downward and inward to the motor M located within the base A. For the purpose of obtaining access to the motor M and its associated parts within the base A, hand holes are provided at suitable points, such as shown in Fig. 1, where the same are shown closed by covers 356 and 351, having handles 358 and 359, respectively.

In carrying out the present invention, it will be apparent that many changes and alterations may be made in the details of the structures and mechanisms shown without departing from the spirit and scope of the invention. We, therefore,

.do not wish to be limited' to the exact details disclosed but aim to cover by the terms of the appended claims all the alterations and modifications which rightly come within the scope of the invention.

We claim:

1. In a machine of the class described, a commodity delivering nozzle, a horizontal rotary conveying table having a series of pockets for holding containers with their open ends upward and bringing them successively to filling position be neath said nozzle, projecting cam rollers on the under side of said table spaced peripherally at regular intervals, a cam shaft journaled adjacent to the under side of said table, a drum cam having a groove for operatively engaging said cam rollers, said groove and cam rollers being operative to advance said table step by step with an intervening rest period following each advance step, means for adjusting said drum cam longitudinally of said cam shaft whereby the position of said table may be adjusted circumferentially relative to said nozzle to bring said container pockets successively in line with said nozzle for filling, and means for supplying charges of the commodity through said nozzle to the containers as they present themselves beneath said nozzle.

2. In a machine of the class described, a commodity delivering nozzle, a horizontal rotary conveying table having a series of holes for holding containers with their open ends upward and bringing them successively to filling position beneath said nozzle, projecting cam rollers on the under side of said table spaced peripherally at regular intervals, a cam shaft journaled adjacent to the under side of said-table, a drum cam having a groove for operatively engaging said cam rollers, said groove and cam rollers being operative to advance said table step by step with an intervening rest period following each advance step, means for supplying charges of the commodity through said nozzle to the containers as they successively present themselves for filling, a member for engaging the bottom of a container in the filling position beneath said nozzle and elevating the same into contact with said nozzle, an elevating cam on said cam shaft, means actuated by said elevating cam to move said engaging member up and down in timed relation to the operation of said supplying means, a rod havingthreaded engagement with said drum cam 

